Apparatus for comparing pressures



ori inal Fiied Ma rch 27, 1943 2 Sheets-Sheet 1 02 5 wmiwwf IN VENTOR HENRY HTTORNEYS.

se dv, 1946.

H. w. GILFILLAN APPmi'US FOR COMPARING PRESSURES 2 Sheets-Sheet 2 INVENTOR Original Filed March Z .5 zfm Patented Sept. 17, 1946 Henry W. Gilfillan, Detroit, Mich, assignor to Chrysler Corporation, Highland Park, Mich, a corporation of Delaware ()riginal application March 27, 1943, Serial No.

error.

480,786. Divided and this application December 31, 1943, Serial No. 516,423

11 Claims.

This application is a, division of Gilfillan et al., application Serial No. 480,786, filed March 27, 1943. Copending application Serial No. 518,829, filed January 19, 1944:, in the name of David M. Borden relates broadly to a type of pumping-limit 2 especially when the plane participates in aerial combat. Accordingly, a coordinated control system, subject in some respects to the pilots supervision, but otherwise as automatic in its reactions as may be, is indicated.

detector such as shown in the drawings as D in o It will have been observed that use has been the present application. The present application made of the ten pumping limit. When the relates to this specific form of pumping-limit decharacteristic curve for a supercharger, operat tector and to certain details thereof that may at some designated speed, is plotted, it is readhave use in other than a pumping-limit detector. ily noticeable that a point is reached where fur- The pumping-limit detector for a supercharger disclosed herein is based on the discovery that pumping limit is reached when a, certain relation is reached between increase in pressure produced by the supercharger and velocity head of gas entering the supercharger, Velocity head is actually a very small quantity in relation to increase in pressure, and thus if a balancing of one against the other is to be obtained as is the case in the present application, it is necessary to find some practical way of multiplyingin effect, the force developed by the velocity head in relation to the force developed by the increase in pressure. The means developed in the invention of the present application for carrying this out is of special advantage with the particular type of pumpinglimit detector disclosed, but may be employed just as well in other situations, where it is necessary to balance a small force against a large force or to make comparisons between large and small forces.

As herein employed, the term power plant embraces the internal combustion engine proper, the propeller connected to the engine, and the supercharger which compresses the relatively rare air for delivery with the fuel to the engine inlet manifold. These units are often interconnected by gearing for simultaneous rotation. For satisfactory performance, it is necessary to correlate a number of variables, such as engine or propeller speed the amount of fuel mxture and the proportions of air and fuel in such mixture delivered to the engine, the actual speed of the supercharger and its ratio to the engine speed, and the pressure at which the fuel mixture is supplied. The wide variations in speed and power loads on the and the variations in the air supply due to changes in density and temperature with changes in altitude, coupled with the inci ents of flight service, make the integra-' tion and resolution. of these variables an extremely difficult task. Independent manual adjustments, made by the pilot or crew in response to indicating dial readings, are too dependent on human frailties and preoccupations to be satisfactory,

thcr reductions in the quantity of air passing through the machine fail to produce proportioncreases in the difference between the dey and inlet pressures. Tins point is somees called the surge point, and, With respect to axial flow compressors, its existence may be explained by considering the character of flow through. the supercharger. Toolow a velocity of the with respect to the rotational speed of iblades and their formation, causes the air to meet the blades at toogreat an angle of attack, aerodynamic how is interrupted and the machine stalls. This condition produces noises and vibrations and pulsations which may cause physical failure of the parts, with attendant disruption of the entire power plant, Accordingly, operation of the supercharger at or beyond the surge point is to be avoided.

On the other hand, the supercharger has the duty of supplying to the engine that quantity of air, under suitable pressure, which is needed under its Wide range of operatin speeds and horsepcwer demands. ince the aircraft operates from sea level to very high altitudes, it is apparent that the density, and therefore the mass, of inducted air is also a variable. Presupposing a supercharger designed to supply enough low density air, compressed to a suitable pressure, for an open throttle condition of the engine, then the samesupercharger may not operate effectively with denser air at the same speed, nor with the rarefied air at a lower speed, since a change in either of these factors may adversely effect the angle of attack.

When the surge points for the same supercharger, subjected to changes in these variables, are plotted, it is found that they lie in or along another curve, which establishes the pumping limit. for the supercharger throughout the range of operating conditions which it may encounter. In practice, it means that; a certain relationship must be maintained between the pressure rise through the machine, and the quantity of air which passes through the supercharger. Mathematically, the relationship may be expressed, with sufiicient accuracy for present purposes, by a simple equation in this form:

where P2 is the pressure of the discharged air;

P1 is the inlet or barometric pressure; p is the density of the inducted air; 1) its velocity; and K, K, are constants. This relation may also be expressed by the equation:

. In one aspect, this invention contemplates a control system in which the supercharger is made to operate within the pumping limit. The principles and means hereinafter discussed in detail will disclose how such result is obtained.

An object of the present invention is to provide improvement in a pumping-limit detector.

Another object is the provision of improve-' ment in a pumping limit detector of the type functioning on a relation of pressure increase and velocity.

A further object is to provide an improved device for balancing or comparing large and small forces against one another.

Additional objects, and the advantages to be derived from the practice of the invention, both in its entirety or by use of its several components,

will become apparent from a perusal of the following description of a preferred embodiment, read in connection with the accompanying drawings.

For the purposes of clarity and simplicity, there are omitted from the drawings representations of various standard parts, accessories, and design details, since these, as such, form no part of the present invention and are here unnecessary for a full presentation of the subject to those skilled in the art. For like reasons, no attempt has been made to illustrate an airplane engine, nor the details of a supercharger, nor themechanism interconnecting the same.

Fig. 1 is a diagrammatic view partially in section of controls for a supercharger; Fig. 2 shows an airplane propeller and pitch control therefor; and Fig. 3 is a sectional view of a pumping limit detector.

In approaching a consideration of the drawings, it may be initially helpful to designate certain of the units by reference letters, the details of which will be presented hereinafter. The

unit A is a rotary member manually operable by the pilot into various positions and, the automatic control features are, to a large extent, governed by the setting of this control instrumentality.

The unit B is a valve including member, manually operable by reason of its connection to the unit A, and further subject to automatic adjustment. The unit C is a valve device responsive to excess changes in the pressure conditions occurring therein. The three units A, B, and C operate conjunctively with a supply of hydraulic pressure fluid entering the units through a filter F, and in such manner as to establish the position of a waste gate or spill valve G positioned in the supercharger delivery line. These units, therefore, modulate the discharge pressure of the supercharger, which is designated by the reference letter S.

The unit D at the left of the figure is a pumping limit detector whose function it is to supervise, and even to overrule, the decisions made by the foregoing units in connection with the setting of the valve G. In other words, the detector D insures the operation of the supercharger S within its pumping limit. The unit E, on the righthand side of the control rotor A, is provided to govern the speed ratio between the supercharger S and the engine (not shown). With this unit is associated a solenoid control valve H and electrical circuits illustrated diagrammatically at the upper right of the figure. The unit M is a mechanism provided to adjust the fuel mixture and it is also responsive 'to the setting of the rotor A. The linkage L, also connected to the rotor A, is connected at its opposite end to the propeller governor (not shown) of the engine in'such manner as to govern the speed of the engine.

Supercharger discharye'pressure regulation Air enters the supercharger S through an inlet line H, flowing through a venturi l2 and thence into the inlet of the supercharger for delivery into a line 13 which is connected to the engine inlet manifold at a point not shown. The line I3 is provided with a lateral or spill pipe I l in which is rotatably mounted the waste gate or spill valve G. An open position of the valve G permits the supercharger discharge to bleed to the atmosphere, a closed position of the valve G directs all of the discharge to the engine manifold, and intermediate positions of the valve permit proportionate withdrawals of the compressed air, either to diminish its quantity or its pressure.

The system is such that the pilot may manually position the gate G. For this purpose a link l5, operable from the pilots position, is connected. by a clevis to a radial arm l6 extending from the outer surface of the unit A. The unit A comprises a pivotally mounted rotatable member having a plurality of cams formed on its external periphery, and internally divided into two chambers by means of inwardly extending sectors H and 18. These are cut away at the center to receive a diametrically extending vane l9, rotatable within and with respect to the casing of the rotor A. There are thus formed pairs of opposed chambers 2| and 22, the chambers in each pair being connected by holes 24 diagonally drilled through the hub of the vane IS. The several chambers 2| and 22 are flooded with hydraulic pressure fluid admitted from a suitable source through the oil filter F and normally blocked off from free flow by valve mechanism hereinafter described. Admission or withdrawal of the pressure fluid to the chambers is effected by piping 25 and 25 entering the pairs of chambers through ducts formed in the rotor casing wall. The vane I9 is, of course, rotatably pivoted for motion relative to the rotor casing, and the unit as illustrated is also provided with a cover plate in order to close the chambers and preclude oil leakage.

i It will be observed that, with the parts in the position illustrated, a left hand movement of the link 15 will effect a counter-clockwise rotation of the rotor A. Since it has been assumed that the chambers 21 and. 22 are blocked against flow of oil, then such movement will drag the vane [9 also in a counterclockwise direction to rotate an attached shaft 21 upon which is mounted the'gate valve G. counterclockwise rotation of the valve will close the lateral l4, and thereby operate to build up rapidly the pressure in the engine inlet line 13. Conversely clockwise rotation of the unit A would, under the same blocked condition for the *vane 19, open the valve G to its limiting position.

portion of the rotor A and its teeth'engage with a rack 29 included in the unit B.

This unit comprises a stationary cylindrical housing 3| (note, for example, the securing lugs 32 at the extreme right). The cylinder 3| is suitably cut away at its mid portion to permit engagement of the teeth of the gear and rack .28 and 29, while the right hand portion 33 is enlarged. Within the bore of the cylinder 3| is a longitudinally movable sleeve 34 having on its external surface the rack 29. The sleeve 34 in turn receives a valve unit 35 provided with a stem 36 which extends to the right hand section 33 where it is coupled with a bellows assembly including the bellows 31 and 33. The left hand section of. the sliding sleeve 34 is provided with ports and fluid pressure line connections adapted to be opened or closed by relative movement of the valve 35. a

Pressure fluid is admitted to the unit B through a pressure line 4! into an inlet chamber 42 connected to the clear space between the valve'discs 43 and 44. Similarports 45 and 41 are provided for normal connection to the space between discs 43 and 48 and 44 and 49 respectively. These last mentioned ports are coupled together by tubes l-which in turn are connected to a drain line 52. The sleeve 34 is also provided, at a radially remote region, with two additional ports 53 and 54. These ports are normally covered by the valve discs 43 and 44. Thus, in the position shown, pressure fluid may enter the region between the discs 43 and 44 via the po 4 but it cannot go anywhere because the exit ports 53 and 54 are blocked by these discs.

The ports 53 and 54 are connected by suitable tubing to opposed chambers formed within the casing of the unit C. This casing has a central shoulder portion 56 receiving a piston 51 which is normally maintained in its centralized position by the hydraulic pressure exerted on its ends, which are in communication with the opposed chambers 58 and 59. Each chamber also receives a spring 6|. The chamber 58 is connected to the chambers 2| of the unit A by the above mentioned piping 25, while the chambers 22 are connected to the chamber 59 by the piping 26. Since, as previously noted, ports 53 and ,54 of the unit B are normally blocked by the valve discs 43 and 44, it will now be apparent why there can be no displacement of the pressure fluid in the chambers 2| and 22, and why thevane l9 must, under these conditions, turn with the unit A.

However, while initial rotation of the manually operable rotor A causes the valve G to shift, due to the drag on the vane l9, rotation of the unit A (in a counterclockwise direction, for example) also draws the longitudinally movable sleeve 34 to the right, due to the intermeshing of the segment 28 with the rack 29. This motionconnects the port'53 with the port 42, and the port 54with the port 41. Accordingly, pressure fluid may now flow through the line 4|, ports 42 and 53, chamber 59, and line 25, to the pair of chambers 22. The chambers 2| are concurrently connected to the drain line 52 through the piping 25, chamber 58, ports 54' and 41, and lateral 5|. Hydraulic pressure is now applied through the chambers. 22 to cause the vane l9 to move in a counterclockwise direction to its limiting position, or, the movement of the rotor A brings into play mechanism causing the rotor l 9 to overtravel.

Conversely, if the rotor A were rotated in a clockwise direction, as by pulling the link l5 to the right, then the sleeve 34 would be shifted to the left. The flow into and away from the rotor would now be reversed, admission being effected through the ports 42 and 54, and discharge occurring through the ports 53 and 45. The remainder of the circuits is the same as heretofore noted. Too rapid overtravel of the vane IS in either rotational direction is forestalled, however, by the operation of the stabilizing unit C. Arapid increase in pressure in either chamber 58 or 59, coupled with a sudden release of hydraulic pressure in the opposite chamber, creates momentarily a substantial pressure difierential on the opposite ends of the piston 51. This pressure differential, therefore, drives the piston into one chamber or the other, to close, by means of abuttin valve discs 62, one or the other of the connections to the ports 53 or 54. Accordingly,

the outwardly flowing oil develops a back pressure in the dischargin chambers 2| or 22, and

in this way prevents the vane l9 from going to its extreme position too rapidly. Obviously, the action of the piston 51 is the same, except for its direction of motion, irrespective of the application of the hydraulic pressure to either side of the vane member I9. Accordingly, the valve G will initially move to that position determined by the manual setting of the control unit A and will thereafter tend to creep forward to its limiting position.

Opposition to overtravel, and restoration of the valve G to a suitable position, is effected through the bellows assembly contained'in the right hand section 33 of the unit B. The bellows 38 is secured at one end to the wall 65, and, at its opposite end, it is joined to the bellows 31, being sealed therefrom by the disc 66. Before sealing, the bellows 38 is evacuated to a very low or negative gauge pressure. The bellows 31, which is free to float in the casing 33, is connected at its opposite end to the valve stem 35, and it is also provided with a vent 61 of small diameter. The space between the bellows and the inner wall of the casing 33 is connected to the supercharger discharge line I3 by a conduit 58. An end wall 59, positioned between the casing 33 and the sleeve 34, and formed with a suitable gland to receive the stem 35, prevents manifold pressure from being exerted on the valve disc 49. Increase in the manifold pressure, caused by closing the gate G, therefore causes an increased pressure to be exerted on the sealed bellows 38, to contract its length. This movement draws the valve stem 36 to the right, and therefore replaces the discs 43 and 44 over the ports 53 and 54. Flow of the hydraulic fluid is accordingly arrested, and the valveG is fixed in position. Conversely, had the rotor A been turned to open the gate G, then the sleeve 34 would have been shifted to the left, and the diminution of manifold pressure would have permitted the bellows 38 to expand. The valve discs 43 and 44 would again have followed after the ports 53 and 54 to restore and maintain the balanced condition.

It is apparent that any condition causing a change in the manifold pressure is reflected by the extension or contraction of the bellows 38, with compatible readjustments of the valve mechanism in the unit B, and the positioning of the gate G. Regulation of the manifold discharge pressure, and its maintenance at a substantially constant value, is thereby effected.

Such regulation is not, however, necessarily instantaneous, because of the action of the bellows 31. Since both interior and exterior of thi bellows arenormally subjected to equal pressures,

byreason cfthe vent 61, relatively slow or small changes in manifold pressure have no significant effect on thebellows 31. When rapid pressure changes tend to occur, as for example, during a power dive or steep climb, the rapid change in the pressure on the exterior of the bellows 31 creates a pressure differential, due to therestrictin effect of the orifice 61. The bellows 31-will then tend to expand or collapse, as the case may be, and thereby add to or subtract from the force acting on the valve stem 36. r I

It will be noted that thebellows 31, which is sensitive to the rate of change of manifold pressure, eifects a rapid adjustment of the valve unit :in anticipating the adjustments to be secured :by'the .bellcws 38. Thus, in a power dive, the manifold pressure increases, transferto a region of denser air. The pressure increase operatesto foreshorten the bellows 31, thus admitting pressure fluid through port 54 to chambers 2i, to open the spill valve G, as previously described. As the pressures within and outside of the bellows?! become equalized, by flow through the orifice 61, the bellows expands. In fact, due to the falling external pressure, caused by the opening of gate G, the bellows may actually be extended beyond its free length. By this time, however, the bellows 38 has taken a new position to govern the setting of the gate, and the combined assembly therefore works to meet a rapid pressure change with a rapid readjustment, followed by rapid dampening to prevent hunting of the valve 35.

Pumping limit detector The pumping limit detector D best shown in Fig. 3 is provided to supervise the performance of the units A, B and C, as just described, and it will be herein treated insofar as it forms an element of the combinations constituting a part of this invention.

The unit D comprises a cylinder 1| provided with left and right hand chambers 12 and 13 of different diameters, and a central bore 14. The chamber 12 is divided into two parts by a diaphragm 1-5, the left hand part being connected to inlet pressure by a pipe 16 leading to the supercharger inlet .l i. The right hand part is connected by a pipe 11 to the venturi l2. The diaphragm 15 is, therefore, subject to an unbalanced pressure proportionate to the pressure drop between the upstream and throat regions of the ventur-i, which pressure tends .to force the diaphragm 15 to the right.

The right hand chamber 13 is divided into three sections by two spaced diaphragms 11a and 18. The middle chamber, between the two diaphragms, is subjected to inlet pressure by a conduit 19 leading to the pipe 16. The right hand section of the chamber 13 is connected to the supercharger discharge line 13 by a pipe 8|, and to the left hand section by a duct 82. Thus, the same high pressure is applied in opposing directions on the diaphragms 11a and 18 against the relatively low resistance of inlet pressure in the space between the diaphragms.

The area of diaphragm 18 is slightly larger than that of diaphragm 11a. Since the inlet pressure in pipe i9 is applied in opposed directions on the diaphragms Tia and 18 in the chamber between these diaphragms, and the outlet pressure in pipe 8i'is. applied in opposed directions on the outer sides .of diaphragms 11a and 18, the net thrust to the left dueto these pressures is a product of the difference in these pressures and the differbecause of the rapid 8 once in the areas of the diaphrag-ms ll-a and 18. Since the diaphragm-13 is only slightly larger in area than the diaphragm 11a, the difference between these areas is small and the force exerted to the left on the valve stem 84 is only a small multiplication of the difference in pressures.

In contrast therewith, the area of the diaphragm 1-5 is larger than that of diaphragm 18 and many times larger than the difference in the areas of th diaphragms 11a and 13. Consequently, the velocity head in the inlet l i measured by the difference in pressures in the pipes 16 and 11 is multiplied considerably by the large area of the diaphragm 1-5 to an appreciable total force to the right on the valve stem 81%. 7

What is accomplished is the use of a small area for one unitiforce and of a large area-tor another smaller unit force to establish a relation between the two unit forces depending upon a multiplica-- tion of the smaller unit force. This. might have been accomplished by the use of a very small diaphragm, but this would increase the possibility of errors very considerably. Instead, I have accomplished the same result by the use of two relatively large diaphragms 11a and 1,8, which "are of slightly different areas and are opposed to one another, so that they have the diaphragm.

This arrangement is of special advantage with the pumping-limit detector disclosedhcrein, for this detector functions by balancing velocity head, a Very small quantity, against pressure difference, :a more appreciable quantity. However, it should be understoodthat this arrangement is not limited to pumping-limit detectors of this type orpumping-limit detectors of any type, for it may be applied as well to other devices.

It should be noted that a bellows 91 is secured to the right end of the chamber 113 and to the outer side of the diaphragm 1.8,. reducing the effective or pressure-responsive area of the outer side of diaphragm. Without the bellows-91 the pumping-limit detector D would operate according to the equation:

P2-P1=K /2pV With the bellowsthe equation is either The diaphragms 11a and 18 have members or portions secured to their inner sides, which abut one another and transmit the forces exerted upon one diaphragm to the otherdiaphragm and vice-versa. I

Interposed between the two chambers 12 and 1 3, and in the bore 14, is a valve unit whose stem 84 abuts both the d-iaphragms 15 and 11a. A centrally located valve disc -85 normally uncovers a port 86., which is connected to high pressure hydraulic fluid by a branch $1. The liquid is thus admitted to the clear space between the disc 85 and another disc 88, which space is connected to the pressure line 4| by a port .89. The previously described drain line '52 is coupled to a port Bi leading to the clear space between the "disc 85 and a third disc 92, communication with the master drain line 94. Another drain line leads through an additional port Q6 tothe :clear space between the discs 85 and 588,110 become effective when the valve assemblyzpushed over to the left. At that time, the

effect of one small 7 for connection to a port 93 in,

nal slot I93.

9 inlet line 87 is coupled to the li' e while the master dra n is connected to the line ll Any sh"ting of the valve stem which makes: the line a drain, and the line 52 a pressure supply line, of course completely reverses the direction of application of force on the vane it of unit A, as heretofore described. I oher wor the val e settings of u it D, in existing pressure condpressure line, v hereby the units A, a; late the setting of the gate G as forme When the settings are reversed, then vane instead of moving the gate G to closed pom..- tion, for example, will move it an open posit on. The detector D may therefore on .pletely l'illillfy th natural inclination of the or its A, B and C in actuating the valve G, the charger discharge pressure.

The detector operates to overrule the waste gate regulator, and reverse its action, when the amount of delivered is so small, with respect to the pressure rise, that the pumping limit of the supercharger is reached. Such a situation may arise under variation in the controlling factors heretofore discussed.

Referring again to the left hand chamber 72 cf the unit D, it will be seen that the force exerted in the right hand direction, which tends to keep the main pressure line in communicaticn with the line ll, is proportional to the workin of the diaphragm "l and to the pressure drop from atmosphere to the Venturi throat l2. The pressure drop is in turn proportional to the density of the air, and its velocity. Hence, the mean effective thrust on the left hand end of the valve stem 3% may be proportioned to the expression: 0 The left hand thrust is similarly proportioned to the pressure rise (Pg-$1), since the middle section of chamber l3 is connected to atmosphere, while the other faces of the differential diaphragms l'lc iii are sub jected to the supercharger dischar e pressure.

Accordingly, under normal conditions of operation, or over that range of pressure quantity ratios within he pumping limit, thedetector D p rinits admission of the hydraulic pressure fluid L to the line ll. The units A, B and C then function as first described, the manifold pressure is regulated, and any excess air delivered at that pressure, which is not needed by the engine, passes to waste through the partially open spil1 valve G. When this relationship changes in such mannor as to cause the supercharger S to approach its pumping limit, the ate rather than being turned to closed po tion in the manner first outlined, will new so ti: rust toward an open position, The resulting reduction of discharge pressure head, by the relief of the compressed air, is reflected in the line and on the diaphragms Tia and id, as well as the bellows 3i and 38. Valve stem tbl may then move toward the right, restoring to line ii its function as a pressure fluid supply line, and thereby making the unit 13 once more the control instrumentality.

It may be assumed that operation of the aircraft causing the detector D to cut in and out of service will be accompanied by other conditions observed by the pilot. He may then elect to shift the link to the extreme right, thereby .to open the gate G, manually, and he may moreover desire to throttle the engine to an even greater extent. For this purpose, the arm it, connected to the link i is vpcovided with a pin illl, to which is attached rod it? formed with a termi- The slot receives a pin lll l confit) , ever, when high altitudes are nected to a linkage 5'95, which is connected in turn to a damper 5G5 pivoted in the manifold line Normal :back and forth motion of the rod lei simply causes the pin i i l to ride in the slot m3. Under these conditions the damper I05 hangs wide open, and is not aifected at all. However, if the link it is pulled to its extreme position, the end of the slot engages the pin iii l, pulling it along to close the damper I06, and thereby additionally throttle the engine. Restoration of the link ii to a normal operating range permits the damper to open, restoring the control ofthe air supply to the units heretofore considered.

Supcrchargerdrive control The supercharger S is driven from the engine through a drive unit H2, which, as herein indicated includesnuid coupling members and gearing permitting the supercharger to run at one or the other of two speed ratios. Normally, the gearing will be set to drive in the low speed ratio. Howencountered, it may be necessary to shift to the higher speed ratio, so that the supercharger may deliver an adequate quantity of air and still operate safely within the pumping limit. The particular drive just referred to is not the subject matter of this invention, and therefore, is not shown in detail. Here, the description is concerned with the control of the drive, and, since a fluid coupling is involved, the control means is made to govern the supply oi hydraulic fluid to the coupling.

There are two hydraulic pressure fluid lines, 2' 53, l Hi, which lead from the unit H to the coupl'ng l2, and a main feeder i it extends from the F to the unit H. When the feeder H5 is connected to the line M3, the unit H2 is in low speed, when the unit H is actuated to couple the lines 5 l5 and i it, the supercharger S is driven through the high speed ratio. Selection of the position of the unit l-I may be effected either manually, or automatically through the unit E. The at comprises a fixed cylindrical casing l2! 3: a movable follower :22 projecting from end thereof, and held in engagement with a cam on the rotor unit A by means of a Hence, atmospheric pressure tends to collapse the bellows withdraw its inner end from engagement with the push pin 52%. At higher altitudes the bellows will expand, due to the lower air density, and may do so even to a point where it can press the pin i255 sufficiently hard to shift the switch till, everything else disregarded. Normally, the parts so proportioned that, at sea level, the maximum lift of the cam 23, brought into by rot on of unit A, is insuficient to offset the contraction of the bellows 125. As higher altitudes are reached, extension of the bellows E25 permits the actuation of the pin I26 diirerent settings of the cam I23, until finally a point is reached where actuation of the rotor A becomes unnecessary, as just pointed out. Thus, theswitch l2? will shift at some predetermined altitude,"established by the setting of the rotor A and the barometric pressure. Or,-stated otherwise, each setting of the rotor A, by the manual lever i5, determines the altitude at which the supercharger may go into high speed.

7 I29, while withdrawal of the pin up, as

The switch I21, as shown in the diagrammatic repetition in the drawings, is of a single pole, double throw type, wherein inward movement of the pin I26 forces the resiliently supported lever I28 into engagement with a high speed contact I26 permits the lever I28 to move forward against a low speed contact I3I. Manual control over the electrical circuit is obtained through a switch having a pivoted arm I33 which maybe selectively set on an automatic control contact I34, a low speed contact I35, or a high speed contact I36. When the arm is in the position shown, the gearing I I2 may be in either high or low ratio; when point I35 is used only a low ratio is available, and when point I36 is connected, the high speed ratio is selected, subject to certain limitations hereafter stated.

The circuits established by the settings of switches I33 and I21 (which will be traced directly) determine whether fluid will flow from line II5, through unit H, to line H3 or line II4. This unit comprises a housing I31 formed with a bore I38 in which is slidably mounted a valve member I39. The feeder line II connects to a port I4I, communicating with the bore I38, while .the lines H3 and H4 are respectively connected to axially spaced ports I42 and I43.

The valve member carries a series of spaced discs which serve to direct pressure fluid to the line H3 or II4, depending upon their relation to the port MI. The structure is so similar to the valves heretofore described that it is believed unnecessary to elaborate thereon. It may, however,'be noted that the unit is formed with additional, similar ports I45 which seem to re-open the feeder II5 to the line from which it otherwise would be blocked. This, however, is desirable, since the short-circuiting connection is taken through a restricted orifice, as shown.

Admission of a limited amount of fluid to the blocked line H3 or II4 assures lubrication and cooling of the coupling then out of service, but the total flow is too small, for power transmission purposes.

The valve member I39 has an extended stem I5I terminating in a olevis I52, the pin of which is positioned in a slot I53 of a lever I54, pivoted on a fulcrum I55. The opposite arm of the lever is formed with a fork I56, in which may ride a pin I51 extending from a rocker segment. The segment, which is centrally pivoted on a stud I59, carries a pair of links I6I at one corner, which extend to a plunger I62 of a solenoid I63. When the solenoid is energized, the plunger is pulled up, thereby to rotate the segment I58 and to bring the links I6I into a substantially vertical position. As will presently appear, such movement simultaneously breaks the energizing circuit, permitting the plunger I62 to drop away. Due to the inertia of the moving parts, however, the segment does not fall back to its starting position, but continues its travel to the opposite upper quadrant from which it started. Thus, each energization of the solenoid shifts the pin I51 up or down.

r This motion is transmitted through the lever I54 to shift the valve stem I5I either down or the case may be. For example, the drawings show the links I6I in the second quadrant and the valve discs I44 so located as to supply pressure fluid to the low speed-line II3. energizing the solenoid I63, links I6I swing to the first quadrant, and stem I5I is pulled down to connect ports MI and I43, thereby supplying Upon ' return. Plunger I62 is .urge of its holding spring 12 high speed line H4, and blocking line II3 except for the reduced lubricating flow alluded to. On the next energization, the motion is reversed and the stem I5I is pushed up to restore it tothe position illustrated.

' The stem I5I carries spaced conductive discs I64 and I65, which respectively bridge either contacts I66 and I61 or contacts I69 and I69, depending upon the position of the valve. Contacts I66 and I69 are connected by a common wire IN to the solenoid I63, the other side of which is grounded.

Let it be assumed that the machine has been running in the lower speed ratio, the parts of the solenoid valve unit H being as shown, and that the pin I26 has just been moved to force the switch arm I28 into engagement with the high speed contact I29, the switch arm I33 then contacting the automatic control point I34. A circuit for energizing the solenoid I63, thereby to shift the valve member 539, is now established as follows:

, From the power source through arm I33, contact I34, wire I12 to arm I28 and high speed contact I29, thence via wire I13 and junction, I14 to wire I15 into the armature I16 of a relay R, then engaging contact I11 connected to wire I18 leading to contact I61.at'stem I5I; thence through disc I64 to contact I66 and wire I1I to the winding of the solenoid I63, to ground and thereupon lifted to pull down the Valve I39 as previously described, the disc I64 being separated from contacts I66 and I61 to break the circuit just traced when the links I6I approach dead center. The disc I65 will accordingly engage contacts I68 and I69 when the parts have come to rest.

When the pin I26 is withdrawn, switch arm I28 engages low speed contact I3I, and a reversal of the fluid connections, to restore the low speed ratio, is effected through the following circuit: From the power source to contact I3I, wire I19, junction IBI, wires I82 and I83, thence through disc I65 and contacts I58 and I6 9'to the solenoid I63.

Let it be assumed that the pilot selects the low speed contact I35 for the switch arm I33. Current then flows through contact I35 and wire I83 to contact I69, thereby to establish a circuit for low speed position of the unit E. If it be assumed that the high speed contact I36 is selected, the solenoid valve unit will (subject to a subsequently stated limitation) remain in the desired position, being actuated through the following circuit: Contact I36, wire I15, .armature I16 and contact I11 of relay R, thence viawire I18 to contact I61, etc.

cludes a coil I85, connected directly to the power source by a wire I86 and a wire I61 leading through a thermostatic" switch I88 positioned in the pipe I3. Thus, the coil I will be energized whenever switch I88 closes at a predetermined temperature.

Armature I16 is then'pulled down against the I89 to engage contact I9l, which leads via wire I92 to junction I8I, and so into the low speed selecting circuit.

The armature I16 is latched into this position by an armature I93 of a second coil I94, which must be I16 to return into engagement with contact I11,

energized to permit the armature Engine regulation The engine of the power plant is supplied with air flowing past the damper Hi6, and fuel which V is later mixed with such air. It is common in the art to include, with the engine, a proportioning device through which the relative percentages of fuel and air are determined and maintained. However, it is desirable to supervise the performance cf such device in response to the manifold pressure, as determined by the instrumentalities heretofore considered. Thus, if the manifold pressure becomes either high or low, a rich mixture is indicated, while at intermediate pressures, the mixture may be lean.

Means for assuring the rich mixture are provided by the unit M, operating in conjunction with the manifold control unit A. The unit M comprises a valve casing 29! enclosing a spring loaded piston 282, whose stem 253 extends beyond the casing for connection to the carburetor controls, not shown;

The casing 2!!! also contains a bore 2% receiving a plunger 205, formed with a stem ace which normally engages the dwell portion between two similar cams 201 on the rotor A. The bore 2% is formed with ports on either side of the head on the plunger 285, one of which is connected by a pipe 285 to the main hydraulic feeder line H5. The other port is connected to a drain line, and it also communicates with the l upper side of the piston 2E2 through a duct 289. Hydraulic pressure therefore urges the plunger 295 to the right, bringing the stem 2535 into engagement with the periphery of the unit A.

The plungerfldfi normally partially uncovers a port 2 below the piston 2&2, thereby enabling pressure fluid from the line 238 'to urge the piston and its stem 2.93 upward. This position, by connection to any suitable linkage, sets the carburetor for operation in the usual manner. If, however, the rotor A is moved to either extreme position, the stem 236 rides up on one or the other of the cams Zill, and moves to the left to block the line 208, and connect the port 2-H to drainage. This permits the piston 262 to drop. If the rotor A is rapidly shifted from one extreme position to the other, the piston 2532 will not, however, be significantlly affected. This is due to the fact that the admission of pressure fluid through the port Eli is slow, in comparison to the drainage rate. Accordingly, the valve unit protects against sudden mixture changes which might be conducive to creating backfires. When the piston 2'52 drops, the corresponding movement of the stem 2% sets the carburetor unitin such position that only a rich fuel mixture can be supplied. Since the extreme movement of unit A corresponds to a high or low manifold pressure, the apparatus therefore achieves the purpose intended.

Under take-oil conditions, a relatively high propeller, and engine, speed are desirable, while under flight conditions it may be better .to .de-

crease the speed. This can :be done by changing the propeller pitch. 7 V

The unit L is therefore provided to adjust the propeller and engine speeds in response to the manifold pressure. The periphery .of the rotor of unit A is formed with a milled cam slot M5, to which is connected a bellcrank lever M6, the upper arm of which is pivoted to a linkf I]. This link extends to a control mechanism 218 fora propeller governor speed control, the propeller being indicated by 21 9. Hence, an extreme movement of the rotor A, representing a high or low manifold pressure, will affect the propeller pitch,

while in intermediate positions the inner end of the lever lid is free to ride in the slot 215. The

slot EIS is advantageously so cut as to insure a definite relationship between engine speed and manifold pressure, the curve being laid out from knowledge of the engine characteristics. In such case, intermediatesettings of the rotor A cause the lever M6 to be'positoned so as to follow the speed and pressure relationship.

It will thus be seen that the present invention provides an integrated control, automatic in operation, for the various components of the power plant, and accordingly relieves the pilot of the necessity-of making a large number of independent adjustments. He is, however, free to supervise many such adjustments by his overriding manual controls, and he may therefore exercise his judgment with considerable latitude. The system is obviously directed to one wherein the supercharger is regulated by control of the discharge pressure, rather than by throttling the supercharger inlet, and any excess of air delivered at the predetermined pressure is accordingly sent to waste. Such plan of control admits of the simultaneous governing of the other related Variables, as hereinabove explained.

While the invention has been described with reference to one embodiment only, it will be apparent that numerous changes and modifications may be made without departure from its principles, or the scope of the following claims.

I claim:

1. A device for comparing a small pressure quantity with a much larger pressure quantity by causing the small quantity to act against a much larger area than that acted against by the much larger quantity, said device comprising first and second diaphragms positioned opposite one another, the pressure-responsive area of the sure quantity to apply force in the opposite direction against the second diaphragm, members secured to the inner sides of the first and second .diaphragms and abutting one another for causing the forces ,to act in opposition to one another and to be resolved to a small force acting in the one direction and being proportional to the product of the much larger pressure quantity and the difference in the pressure-responsive areas of the first and second diaphragms, a third diaphragm, means ,for applying the small pressure quantity against the third diaphragm in the said opposite direction, and means connecting the third diaphragm with the first and second diaphragms.

.2. A device for comparing a large difference in pressures between two regions at high and low pressures with a small difference in pressure between two regions at high and low pressures; said device comprising first and second diaphragms having inner and outer pressure-responsive areas and being positioned with inner pressure-responsive areas opposite one another, the first diaf phragm having larger pressure-responsive areas 'means connecting the diaphragms for causing the said large difference in pressures to produce aresultant force acting in a direction from the first diaphragm toward the second diaphragm and proportional to the product of the said large difference in pressures times the difference between the pressure-responsive areas of the first and second 'diaphragms; a third diaphragm disposed on the outer side of the second diaphragm in spaced relation thereto; means for applying against the side of the third diaphragm facing the second diaphragm the low pressure of one of the two regions having the low difference in pressures; means for applying against the other side of the third diaphragm the high pressure of the other of the two regions having the low difierence in pressures, the last mentioned high and low pressures producing a resultant force directed toward the first and second diaphragms and being proportional to the product of the area of the third diaphragm and the small difference in pressures; and means connecting the third diaphragm with the first and second diaphragms for balancing the resultant force produced at the third diaphragm against the resultant force produced. at the first and second diaphragms.

3. A device for comparing a large difierence in pressure between two regions at high and low pressures with a small difference in pressures between two regions at high and low pressures; said device. comprising first and second diaphragms having inner and outer pressure-responsive areas I and being positioned with inner pressure-responsive areas opposite one another, the first diaphragm having larger pressure-responsive areas then the second; means for applying in opposite directions against the inner pressure-responsive areas of the first and second diaphragms the low pressure of the one of the two regions having a large difference in pressures; means for applying in opposite directions against the outer pressureresponsive areas of the first and second diaphragms the high pressure of the other of the two regions having a large difference in pressures; members secured to the inner sides of the first and second diaphragms and abutting one another for causing the said large difference in pressures to produce a resultant force acting in a direction from the first diaphragm toward the second diaphragm and proportional to the product of the said large difference in pressures times the difference between the pressure-responsive areas of the first and second diaphragms; a third diaphragm disposed on the outer side of the second diaphragm in spaced relation thereto; means for applying against the side of the third diaphragm facing the second diaphragm the low pressure of one of the two regions having the low difference in pressures; meanszfor applying against the other side of the third diaphragm 16 the high pressure of the other of the two regions having the low difference in unit pressures, the last mentioned high and low pressures producing a resultant force directed toward the first and second diaphragmsand beingproportional to thev product of the area of the third diaphragm. and the small difference in pressures; and means connecting the third diaphragm with the first and second diaphragms for balancing the resultant force produced at the third diaphragm against the resultant force produced at the first and second diaphragms.

4. A device for comparing a large difference in pressures between two regions at high and low pressures with a small difierence in pressures between two regions at high and low pressures, said device comprising a first means providing inner and outer pressure-responsive areas, a second means providing inner and outer pressure-responsive areas somewhat larger than the pressureresponsive areas of the first means, the two inner pressure-responsive areas being opposite one another, means for applying in opposite directions against the inner pressure-responsive areas of the first and second means the low pressure of the one of the regions having a large difference in pressures, means for applying in opposite directions against the outer pressure-responsive areas of the first and second means the high pressure of the other of the two regions having a large difference in unit pressures, means connecting the first and second means for causing the said high and low pressures to produce a resultant force acting in a direction from the second means toward the first means and proportional to the product of the said large difference in pressures times the difierence between the areas of the first and sec- 0nd means, a third means having opposed pressure-responsive areas, means for'applying against one area of the third means the low pressure of the one of the two regions having the low difference in pressures, means for applying against the other area of thethird means the high pressure of the other of the two regions having the low difference in pressures, the last mentioned high and low pressures producing a resultant force opposed to the resultant force produced at the first and second means and being proportional to the area of the third means times the small difference in pressures, and means connecting the third means with the first and second means for balancing the aforesaid resultant forces.

5. A device for comparing a small pressure difference representing velocity head of gas entering a supercharger with a large pressure difference equal to the pressure of gas discharged from the supercharger minus the pressure of gas entering the supercharger, said device comprising a first means providing inner and outer pressure-responsive areas, a second means providing inner and outer pressure-responsive areas somewhat larger than the pressure-responsive areas of the first means, the two inner pressure-responsive areas being opposite one another, means for applying the pressure of entering gas in opposite directions against the inner pressure-responsive areas of the first and second means, means for applying the pressure of discharged gas in opposite directions against the outer pressure-responsive areas of the entering a supercharger represented by a small pressure difierence between a pressure at one region of entering air and a pressure at another region of entering air, with a large pressure difference between the pressure of air discharged from the supercharger and the pressure of entering air, said device comprising first and second diaphragms having inner and outer pressure responsive areas and being positioned with inner pressure-responsive areas opposite one another, the first diaphragm having larger pressure-responsive areas than the second, means for applying the pressure of entering air in opposite directions against the inner pressure-responsive areas of the first and second diaphragms, means for applying the pressure of discharged air in opposite directions against the outer pressure-responsive areas of the first and second diaphragms, means connecting the diaphragms for producing a resultant force proportional to the difference in pressure-responsive areas of the first and second diaphragms times the large difference in pressure 7 between discharged air and entering air to produce a resultant force acting in a direction from the first diaphragm toward the second diaphragm, a third diaphragm, means for applying against the opposite sides of the third diaphragm the pressures having the small difierence in pressures representing the velocity head of entering air to 18 discharged from the supercharger and pressure of entering air, to reverse control apparatus for the supercharger by switching certain lines of the control apparatus from a source of fluid pressure to exhaust and vice versa, said detector comprising a first means having inner and outer pressure-responsive areas, a second means having inner and outer pressure-responsive areas larger than those of the first means, means for applying the pressure of entering air against the inner areas of the first and second means, means for applying the pressure of discharged air against the outer areas of the first and second means, means connecting the first and second means to produce a resultant force proportional. to the large pressure difference times the difierence between the pressure-responsive areas of the first and scond means, a third means having opposed pressure-responsive areas, means for applying the pressures having the small difierence in pressure against the areas of the third means to produce a resultant force opposed in direction to the resultant force produced at the first and second means, and means connecting the third means with the first and second means for balancing the resultant forces against one another and including valve means for switching the said certain lines of the control apparatus from pressure to exhaust and vice versa, depending upon the relative sizes of the resultant forces produced at the first and second means and at the third means.

8. A device as specified in claim 3, the outer pressure-responsive area of the first diaphragm being smaller than the inner pressure-responsive area of the first diaphragm.

9. A device as specified in claim 3 and further including a bellows means fixed to the outer side of the first diaphragm for making the said outer pressure-responsive area smaller than the inner pressure-responsive area of the first diaphragm.

10. A device as specified in claim 5, the outer pressure-responsive area of the second means being smaller than the inner pressure-responsive area of the second means.

11. A device as specified in claim 5 and further including a bellows means fixed to the outer side of the second means for making the outer pressure-responsive area of the second means smaller than the inner pressure-responsive area of the second means.

HENRY W. GILFILLAN. 

